Compact Seismic Source for Low Frequency, Humming Seismic Acquisition

ABSTRACT

A compact seismic source for seismic acquisition generating a humming signal includes a casing and a low-frequency reciprocating drive. The casing defines a fluid tight chamber and comprises a first casing section and a second casing section of roughly equal mass. The drive is disposed within the fluid tight chamber and, in operation, reinforces the natural reciprocating oscillation of the first and second casing sections relative to one another at a low seismic frequency. In one aspect, this action omni-directionally radiates the low frequency, humming seismic signal. On another aspect, the compact seismic source is substantially smaller than the wavelength of the low seismic frequency. Such a compact source may be deployed to omni-directionally radiate a low frequency, humming seismic signal during a seismic survey.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority, under 35 U.S.C. § 119(e), ofProvisional Application No. 61/942,001, filed Feb. 19, 2014,incorporated herein by this reference.

DESCRIPTION OF THE INVENTION Field of the Invention

The present invention pertains to marine seismic sources and, moreparticularly, to a compact seismic source for low frequency, singlefrequency, seismic acquisition.

BACKGROUND OF THE INVENTION

A relatively recent development in seismic acquisition is low-frequencyacquisition at a single frequency. This is sometimes referred to as a“humming acquisition”. More precisely, “humming” is using anon-impulsive controlled-frequency source that generates substantiallyall of its energy at a single frequency. Due to practical stabilitylimitations the source may instead perform a controlled or uncontrolleddrift within a narrow frequency range, typically staying within plus orminus one tenth of an octave around the nominal frequency. This issometimes what is called “monochromatic” or “near monochromatic”, forexample in U.S. application Ser. No. 13/327,524.

Humming acquisition may occur in several different ways. For example,stepped humming is a sequential humming acquisition in which a singlesource steps over a set of two or more discrete frequencies, one at atime. The time spent moving between frequencies should be very smallcompared to the time spent at each frequency. Chord humming is a hummingacquisition in which one or more sources simultaneously hum atdiffering, discrete frequencies. More information is available in U.S.application Ser. No. 13/327,524.

Seismic sources such as those presented in the aforementionedapplication are suitable for their intended purpose. However, the art isalways receptive to improvements or alternative means, methods andconfigurations. The art will therefore well receive the seismic sourcedescribed herein.

BRIEF DESCRIPTION OF THE DRAWINGS

The accompanying drawings, which are incorporated in and constitute apart of this specification, illustrate embodiments of the invention andtogether with the description, serve to explain the principles of theinvention. In the figures:

FIG. 1 depicts one particular embodiment of a low frequency, singlefrequency seismic source.

FIG. 2 illustrates seismic acquisition using the seismic source of FIG.1 in one particular embodiment.

FIG. 3A-FIG. 3B graph selected aspects of the performance of the seismicsource in FIG. 1.

FIG. 4A-FIG. 4C graphically illustrate selected aspects of designtradeoffs for the seismic source in FIG. 1.

FIG. 5A-FIG. 5C depict one particular embodiment of a low frequency,single frequency seismic source.

FIG. 6A-FIG. 6C illustrate one particular embodiment including a valvingsystem to allow stepwise control of the internal compressible gas volumeof the seismic source in FIG. 1.

FIG. 7 depicts another particular embodiment of a low frequency, singlefrequency seismic source alternative to that shown in FIG. 1 and in FIG.5A-FIG. 5B and FIG. 5C.

DESCRIPTION OF THE EMBODIMENTS

Reference will now be made in detail to the present embodiment(s)(exemplary embodiments) of the invention, an example(s) of which is(are) illustrated in the accompanying drawings. Wherever possible, thesame reference numbers will be used throughout the drawings to refer tothe same or like parts.

Turning now to FIG. 1, one particular embodiment of a low frequency,humming, compact seismic source 100 is shown. A compact source is a termused by those versed in the art of acoustics and in the present contextto denote a source whose dimensions are much less than the smallestwavelength of its emitted signal and which consequently radiatesomni-directionally in a homogeneous isotropic fluid such as the water inwhich a marine seismic survey is conducted.

The term “humming” does not mean in this context that the seismic sourceis capable of producing seismic signals of only a single frequency,although that may be the case in some embodiments. It instead refers toa mode of operation in which the seismic source emits signals of only asingle frequency for a limited duration at some point in its operation.That is, at some point in its operation, a non-impulsivecontrolled-frequency seismic source generates substantially all of itsenergy at a single frequency for a limited duration. In one embodiment,“substantially all of its energy” means 95% of its energy within ±0.1octave. The duration will typically be sufficiently long that itsinverse exceeds the frequency resolution required for the task in handand will be much longer than one cycle of the emitted signal.

For example, the discussion of humming acquisition set forth abovecontemplates an acquisition in which the source steps over a set of twoor more discrete frequencies, one at a time. Such a source is considereda humming source within the context of this disclosure because it emitssignals of only a single frequency for intervals of time much longerthan the period of the seismic signal during its operation. This is trueeven though it does so more than once employing more than one frequencyat different times.

Note also that “low frequency” is “low” as considered within the seismicsurveying art. In this context, “low frequency” is less than about 6-8Hz and, more typically, less than about 4 Hz. The term “about” is arecognition that in acquisition seismic sources may come out ofcalibration or be poorly calibrated, simultaneously radiate atadditional frequencies (for example from harmonics or from noise from acompressor), or that their signals can drift or in other ways deviatefrom what is desired. Thus, the term “about” means that the actualfrequency is within the operational error acceptable to those in the artrelative to the desired frequency of acquisition.

Returning to FIG. 1, the seismic source 100 is, more particularly, acompact seismic source. The seismic source 100, in operation, generatesa signal of primarily a single frequency at any time. That is, theseismic source 100 is a “humming” source as humming is described above.The seismic source 100 comprises a casing 105 and a low-frequencyreciprocating drive 110 disposed within the casing 105 in a mannerdescribed more fully below.

The casing 105 is comprised of two casing sections 115, 120. They areconstructed of conventional materials well known to those in the art.The first and second casing sections 115, 120, when assembled, are ofroughly equal mass. What constitutes “roughly equal” may vary fromembodiment to embodiment because equal masses give the lowest possibleresonant frequency for a given overall size and mass of the seismicsource 100 as a whole. Thus, embodiments in which the seismic source 100emits lower frequencies will seek to have more equal masses whileembodiments emitting less low frequencies may tolerate greaterinequality in the masses. In the illustrated embodiments, the two massesare within ±10% of one another.

Each of the sections 115, 120 includes a respective domed end 125, 130on the end most distal from the mid-point of the seismic source 100. Inthe illustrated embodiments the domed ends 125, 130 are “hemispherical”.The ends 125, 130 are domed (i.e., have smooth convex profiles) toreduce hydrodynamic drag during reciprocation. In general, if the domeis considered as being half an ellipsoid of rotation with the major axisas the axis of rotation, and with that axis along the axis of thesource, the larger the ratio of major to minor axis (i.e., the morepointed the ellipsoid), the less the drag.

However, other considerations mitigate for the hemispherical design ofthe domes. For example, the hemispherical shape is easy to manufactureand gives most of the drag reduction without causing problems ofside-loading if the device is at an angle to the tow direction.Additional information regarding the shape of the domed ends 125, 130may be found in U.S. application Ser. No. 12/980,527. Note thatalternative embodiments may employ different domed shapes for the ends125, 130.

The casing 105 defines a fluid tight chamber 145. The first and secondsections 115, 120 are joined by a sliding fluid-tight seal 150 allowingrelative motion between the two sections 115, 120. The slidingfluid-tight seal 150 of the embodiment in FIG. 1 is defined by thesealing element 152 sliding across the smooth sealing faces 135, 140 ofthe two sections 115, 120. Note that the outer diameter of the firstsection 115 is stepped down at the seal 150 to maintain a smooth outerprofile for the seismic source 100. While this has a salutary effect onthe operation of the seismic source 100, it is not necessary to thepractice of the invention.

The sliding fluid-tight seal 150 may comprise any suitable sealingtechnique known to the art, providing it permits the sliding engagementof the sections 115, 120. In the illustrated embodiment, the sealingelement 152 is a spring-energized polyethylene lip seal such as is knownin the art. In other embodiments, the sealing element is an elastomericlubricated O-ring. The sealing faces 135, 140 are typically surfacedwith some kind of chrome alloy or other similar material to provide asmooth hard sealing surface.

The low-frequency reciprocating drive 110 is disposed within the chamber145. The disposition should maintain the mass distribution of thesections 115, 120 so that the mass of the two sides across the midlineof the seismic source 100 are roughly equal. In the illustratedembodiment, an excitation actuator 155 is disposed in the second casingsection 120. The excitation actuator 155 is mechanically linked to acentered push-pull rod 160 at one end 165 thereof. The push-pull rod isaffixed to the first casing section 115 at a second end 170 thereof.

In the illustrated embodiment the push-pull rod 160 is supported by twobearings 175 mounted upon stanchions 180 in the second half 120 and astanchion 185 in the first half 115. Note that the push-pull rod 160does not move relative to the first half 115 and so no bearing is neededfor the stanchion 185. These types of supports may be omitted in someembodiments.

The seismic source 100 has a source 133 of compressed gas operationallycoupled to the chamber 145. In some embodiments, this gas source may bea gas reservoir of compressed gas housed within the chamber 145 as shownin FIG. 1. In other embodiments, the compressed gas reservoir may behoused outside of the seismic source 100, say onboard the tow vessel(not shown), and the compressed gas delivered to the seismic source 100by way of an umbilical (not shown), for example. With respect to theumbilical, if it attaches to either of the sections 115, 120 it shouldnot impede their reciprocating motion. It will not normally do so if thetow line is close to the vertical at the point of attachment or if thetow line is elastic.

The compressed gas is used to adjust the internal gas pressure of theseismic source 100 to compensate for gas leaks, temperature changes, andother water conditions. These kinds of adjustments may be desirable tokeep the device on its desired resonant frequency while maintaining adesired tow-depth window. In some embodiments, the casing 105 may housea valve mechanism (not shown) to release gas to the externalenvironment, in order to lower the internal gas pressure of the seismicsource 100. Alternatively, in some embodiments, the internal pressure inchamber 145 may be lowered by means of a pump (not shown) that can forcegas back into the gas reservoir 133.

The gas may be chosen to be oxygen-free to avoid accidental combustionwhen under pressure. Nitrogen is preferable to air in this respect, asis known to those versed in the art. Other inert gasses with a loweradiabatic ratio than nitrogen may also be used to lower the resonantfrequency. For example, a gas like sulfur hexafluoride may be used andbecause of its low adiabatic index it could allow lower frequencies tobe achieved.

More particularly, internal gas spaces of the seismic source 100 arenormally pressurised to match the external hydrostatic pressure. This isdone by filling these internal spaces with an inert gas. The inertnature of the gas avoids the danger of fire which would increase withpressure if these spaces were filled with air. Nitrogen is a suitablealternative to air.

The compact seismic source 100 radiates a very low-frequency seismicsignal, and its resonant frequency depends inversely on the adiabaticcompressibility of the gas within it. That means that the less stiff thegas appears in response to rapid changes of volume, the lower theresonant frequency will be. To this end, it may be advantageous to fillthe seismic source 100 with a gas selected for having high adiabaticcompressibility.

This will be directly proportional to the so-called adiabatic index ofthe gas, which is to say the ratio of its principal specific heat atconstant pressure to that at constant volume. This ratio is smaller forgases whose molecules have more degrees of freedom of vibration, beingequal to about 1.67 for a monatomic gas, 1.4 for a diatomic gas such asnitrogen, and decreasing asymptotically towards unity for morecomplicated molecules with many degrees of freedom. For example sulphurhexafluoride is an inert gas with an adiabatic index of about 1.09, or28% lower than nitrogen.

A source 100 filled with sulphur hexafluoride will thus have a resonantfrequency significantly lower than the same source 100 filled withnitrogen. Those of skill in the art having the benefit of thisdisclosure will appreciate that mixes of two or more gasses could alsobe used, and adjusting the proportions of the gas mixture (for example,by releasing different gasses from two or more gas reservoirs) providesanother way to adjust the device's resonant frequency at a given towdepth. Care should be taken in the design of such a device because thespeed of sound in a gas is equally dependent on its adiabatic ratio. Theinternal spaces must be designed to avoid standing acoustic waves withinthe seismic source 100 since these may interfere with its operation.More specifically if the internal space 145 is close to being anintegral number of half-wavelengths long at the intended operatingfrequency of the source, then the internal gas will present asignificant (high value) impedance at this frequency and the naturalfrequency of the system will shift towards higher frequencies. However,if the internal space 145 is close to being an odd number ofquarter-wavelengths long at the intended operating frequency of thesource then the internal gas will present a very low value impedance atthis frequency and the natural frequency of the system will shifttowards lower frequencies.

Some embodiments may also implement short-term, minor adjustments of thefrequency by adjusting the phase of the feedback of the excitationactuator 155. This control may be exerted by an electronic controller157 housed in the chamber 145. In this particular embodiment, theelectronic controller 157 includes a power source and associatedelectronics not otherwise shown. The electronic controller 157 mayalternatively be housed outside the seismic source 100, perhaps on thetow vessel, and transmitted to the seismic source 100 via, for example,an umbilical.

The depiction of the electronic controller 157 and the compressed gassource 133 in FIG. 1 is conceptual only. The placement, construction,and mounting of the electronic controller 157 and the compressed gassource 133 are subject to the design considerations mentioned. Examplesof these considerations include, for example, weight distribution andwater tightness for the seismic source 100 as a whole. Those in the arthaving the benefit of this disclosure will appreciate theseconsiderations and how to deal with them in a given implementation.

Some embodiments may also include one or more interior compartments (notshown in FIG. 1; an example is shown in 620), or auxiliary external gasspaces (not shown), that could be sealed off from the space 145 oropened to it by servo or hydraulically controlled valves (not shown inFIG. 1; an example is shown in 605), allowing the resonant frequency tobe controlled by changing the compressibility of the gas volume definedthereby. This mechanism would provide a way to quickly jump back andforth between two or more frequencies while keeping the seismic source100 at an approximate constant depth. Smaller changes in volume could beused to re-center the central resonant frequency as needed, allowing thecompressed-gas reservoir to be tapped less frequently. Thecompartments/gas spaces could be organized into a “powers of 2”hierarchy so that a wide range of resonant frequencies could bespecified by opening and closing various combinations of compartments.

As is apparent from the discussion above, the frequency of the marineseismic source will depend on, among other factors, the volume of gasthat it contains. The frequency will depend inversely on the square rootof this volume. This dependence comes about because of the variation inpressure of the gas as the two sections 115, 120 of the casing 105 moverelative to one another. The source frequency will depend on the rate atwhich this pressure changes with casing position. It is thereforepossible to change the frequency by changing the volume of gas whosevolume changes with casing displacement.

Consider the embodiment of 600 in FIG. 6A-FIG. 6C. The change in gasvolume may be effected by introducing gas-tight bulkheads 605 into eachhalf 115, 120 of the casing 105 with large ports 610. The ports 610 maybe opened or closed to either allow free flow of gas across the bulkhead605 if open or to prevent flow if closed. Any such bulkhead 605 shouldbe stiff enough to prevent it from bowing significantly in response tothe difference in gas pressures on its two faces that will occur whenthe casing sections 115, 120 move. The areas and shapes of the ports 610must be such as to present negligible flow resistance to the gas whenthey are open.

A suitable arrangement of bulkheads 605 is conceptually illustrated inFIG. 6A. Each of the casing sections 115, 120 has its internal volume615 divided in two parts 620 by a bulkhead 605. Each bulkhead 605 ispenetrated by the push-pull rod 160 which passes through a seal 625allowing it to move axially with little or no resistance in a mannerwell known to those versed in the art.

When the ports 610 are open, the resonant frequency of the source 600 isnegligibly affected by the presence of the bulkheads 605. When the ports610 of one bulkhead 605 are closed and those of the other are open, theinternal gas volume whose volume varies with the motion of the casing105 is effectively reduced by a quarter, which increases the resonantfrequency by a factor of

$\sqrt{\frac{4}{3}}$

relative to the frequency when all ports 610 are open. If the ports 610in both bulkheads 605 are closed, the resonant frequency is increased bya factor of √{square root over (2)} compared to its value when all ports610 are open.

The bulkheads 605 and the ports 610 may for example be shaped asfollows: A bulkhead 605 consists of a flat disc 630 with two portapertures 635 as shown in FIG. 6B. A rotor 640, shown in FIG. 60, ismounted co-axially with and in contact with the bulkhead 605. The rotor640 rotates so that its wings 645 cover the port apertures 635 at twoangular positions and leave them clear at two others. In the closedposition, the rotor 640 seals the port apertures 635 against fluid flowtherethrough. In combination, the bulkhead 605 and rotor 640 form avalve 650 that, when in the open positions, allows flow through an areaapproaching half the area of the disc 630.

In the illustrated embodiment, the port apertures 635 are shaped likewhat might be called “truncated wedges”. Alternative embodiments mightchoose other shapes for the port apertures 635. For example, someembodiments might shape the port apertures as circles or ovals and stillother shapes might be used. The design of the rotor 640 might also bechanged to accommodate the change in the shape of the port apertures 635in these embodiments.

In an alternative embodiment (not shown), casing 145 contains interiorcompartments that do not extend across the push-pull rod 160,eliminating the need for seals 625. In this embodiment one or morebulkheads 605 control whether or not the gas inside an interiorcompartment is in fluid communication with internal space 145. Aninterior compartment disposed in this way is particularly suitable formaking smaller adjustments to the compressible gas volume (i.e. a fewpercent, instead of the 25 percent for the axially disposed bulkheadsshown in FIG. 6A). Larger adjustments may be achieved if there aremultiple internal spaces, each controlled by bulkhead(s), and these areused additively.

Referring back to FIG. 1, in the illustrated embodiment, an umbilical(not shown) is fitted to the seismic source 100. Compressed gas andvarious control signals are sent to the seismic source 100 and itscomponents via this umbilical. Similarly, outputs from a number ofsensors used to detect relative position and other parameters, forexample, are transmitted back up to the surface through the umbilical.

In an embodiment, the two sections 115, 120 of the seismic source 100will naturally vibrate at a resonant frequency defined chiefly by theirmasses plus the added mass of entrained fluid and the reciprocal of thecompressibility of the gas space 145. The excitation actuator 155, inoperation, pushes and pulls the first section 115 relative to the secondsection 120 in a manner that reinforces that natural reciprocatingoscillation. That is, the excitation actuator 155 operates and iscontrolled to operate to ensure that two sections 115, 120 oscillate atthe natural, resonant frequency of the seismic source 100. This causesthe seismic source 100 radiate a low frequency, single-frequency seismicsignal at the natural resonant frequency of the two sections 115, 120.

The resonant frequency of the two sections 115, 120 is a function of thedepth at which the seismic source 100 is towed because thecompressibility of the gas in the space 145 depends inversely on itspressure which will be equal to the hydrostatic pressure of thesurrounding fluid. The resonant frequency of the seismic source 100therefore can be controlled by adjusting the tow depth. Changing thedepth will change the hydrostatic pressure to which the seismic source100 is subjected. This will, in turn, affect the relative positions ofthe two sections 115, 120.

More particularly, if left uncontrolled, the relative positions of thesections 115, 120 will change in response to depth changes in such a waythat the internal pressure of the seismic source 100 stays equal to theexternal, hydrostatic pressure. Note that if depth changes sufficiently,the responsive position change could continue in some circumstancesuntil the seal 150 reaches the end of its travel. Hard stops (not shown)will therefore normally be provided to prevent the two sections 115, 120from coming apart or colliding. Accordingly, the mass of gas within thechamber 145 may be controlled to maintain the relative positions of thetwo sections 115, 120 so that the sealing element 152 is maintained nearthe center of the sliding surface 140. This is one use for thecompressed gas source described above.

The seismic source disclosed herein is dedicated to a low frequency,single frequency type of acquisition. It does not provide signals of thekind known in the art as “broadband swept-frequency” signals.Accordingly, the design can be considerably simplified and the devicelightened by omitting elements of broadband sweeping sources and itssize compacted. Of particular note is eliminating the variable-stiffnessgas spring and associated squeeze piston(s) used in broadband sweepingacquisition as shown in U.S. application Ser. No. 12/995,763.

One advantage of the size of the compact seismic source 100 is that itradiates the seismic signals it emits “omni-directionally” as is thesignal 200 shown in FIG. 2. More particularly, the seismic source 100radiates an acoustic seismic signal 200 omni-directionally because it ismuch smaller than the wavelengths of the frequencies that it radiates.Note, however, that the wavelengths of the signal being radiated (380 mor greater) are so large that the seismic source 100 could be severaltimes its likely size and still be a compact, omni-directional, acousticsource. In this particular embodiment, the low-frequency seismic signal200 is in the range of 0.5-2 Hz. As discussed herein, the signal emittedis omni-directional because it radiates a signal in all directions (inthree dimensional space) at substantially the same frequency andmagnitude.

The operation of the embodiment in FIG. 1 is constrained by the slidinglength of the sealing face 140, push-pull rod 160 travel, maximumvelocity that the sealing element 152 can tolerate, and device volume.The low end of the achievable frequency range will depend on the volumeof the space 145 and the masses of the casing halves 115, 120. Assume avolume of order 10 cubic meters and a total mass of order 30 tons. Thefrequency would vary with depth roughly as shown in FIG. 3A. Theacoustic output would also vary strongly as shown in FIG. 3B, partlybecause the source, like any compact acoustic source, is a lessefficient radiator at lower frequencies and partly because of thesurface ghost. A surface ghost is caused by the surface of the water,which acts as an acoustic mirror, causing “ghost” effects in recordedseismic data.

At frequencies below about 2.4 Hz (i.e., depths down to about 180 m) theoutput is limited by push-pull rod 160 stroke and, above this, by sealvelocity—i.e., the relative velocity with which the seal attached to thecasing moves over the sealing surface of the piston. The scale in FIG.3A-FIG. 3B is referenced to dB re 1 μPa at 1 m, not re 1 μPa/Hz, becausethe seismic source is emitting a continuous signal. To get the output indB/Hz simply add 20 Log₁₀(T) to the scale, where T is the hum durationin seconds.

The conventional acquisition-geophysicist's measure of dB/Hz, whichintegrates the total energy in a “shot”, starts to be less meaningful inthis single-frequency context in which the signal may emanate forminutes or even hours instead of the 10-16 seconds of a standard airgunrepeat interval. Since the seismic source 100 will be competing withcontinuous random background noise whose spectrum is measured in powerper unit bandwidth, dB re 1 μPa/√Hz, it will be more useful to measurethe acoustic power divided by its bandwidth. The seismic source 100should therefore maintain a stable frequency to minimize its bandwidthand thus maximize its power per unit bandwidth.

The illustrated embodiments achieve frequency stability of 2% or better,which determines the bandwidth. So, for example, the bandwidth is about0.02 Hz for a 1 Hz signal, and so on. This assumes that the signals willlast longer than the inverse of the bandwidth (i.e., longer than about50 seconds). Thus, to get the output in dB re 1 μPa/√Hz, add 10Log₁₀(1/B) to the dB figure re 1 μPa, where B is the bandwidth.

For example, suppose the embodiment of the seismic source 100 discussedabove is operated at 23 m depth. This will allow it to emit asingle-frequency signal at 1 Hz. From FIG. 3A, the source would produce185 dB re 1 μPa at 1 m. Add 17 dB to correct for bandwidth and themeasure is 202 dB re 1 μPa/√Hz. Thus, at 1 m one would have asignal-to-noise ratio of 102 dB if the background noise level were 100dB re 1 μPa/√Hz. This will decline to 13 dB at a distance of 30 km,based on an assumption of simple spherical spreading. Accordingly, witha stable frequency, the seismic source 100 can generate an adequatesignal for seismic acquisition compared to background noise.

However, other design parameters may also be used to define the outputof the seismic source 100. The factors determining its lowest frequencyare the masses of the casing halves 115, 120, the area of cross sectionof the casing half 115 at the sealing face 140, and the casing gasvolume 145 (it decreases with increase in either). The constraints onits output amplitude are push-pull rod 160 stroke; sealing element 152velocity; and the sliding length of the sealing face 140.

For this discussion, the seismic source 100 will be designed to achieve0.7 Hz frequency at 25 m. The contour plot in FIG. 4A shows how theresonant frequency will behave as a function of the casing radius 141and casing length 142. The scales run from a radius equal to 0.8-1.6 mand a length equal to 6-12 m. The individual contour lines give thelocus of possible radius/length combinations for a particular frequency.Thus, the embodiment of FIG. 1 can achieve 0.7 Hz with a length ofapproximately 9 m.

Note from FIG. 4A how little effect the casing radius 141 has on theresonant frequency. This is for two reasons. Firstly, the moving massconsists almost entirely of mechanical mass, with only a smallcontribution from fluid added mass. Secondly, the mechanical mass hasbeen set to be proportional to casing volume, so that increased casingradius 141 (which increases the spring stiffness of the gas cavity) iscompensated by increased mass.

Turning now to output level, setting the length at 9 m and increasingthe stroke in proportion to that length (La from ±0.2 m to ±0.3 m) toget the frequency right, FIG. 4B graphs far-field output (i.e.,accounting for the effect of the free-surface ghost) in dB re 1μPa/√Hz@1 m (i.e., in units allowing comparison with background noise).FIG. 4B illustrates that this design at 0.7 Hz can very nearly match theoutput of the previous example discussed above (i.e., relative to FIG.3A-FIG. 3B) operating at 1 Hz. This can be done without increasing thecasing radius 141, and instead increasing the push-pull rod 160 stroke.Alternatively, one could retain the original stroke and increase thecasing radius 141, as shown in FIG. 4C.

Some implementations of the embodiment of FIG. 1 might impart excessiveaccelerations on electronics and/or fail to provide a stable locationfor a tow point and/or umbilical attachment. An alternative design wouldhave a central stable section with a moving nose on each end. One suchdesign is presented in the embodiments of FIG. 5A-FIG. 5B. FIG. 5B is aside view of the mechanical linkage 515, while FIG. 5A shows a top viewof the mechanical linkage 515.

This seismic source 500 differs from the embodiment of FIG. 1 in that itincludes a stationary section 505 with a tow point 510 to which a towline 511 may be attached. Note that the first and second sections 115,120 still reciprocate relative to one another at the sliding fluid tightseal 150. The functional relationship between the stationary section 505and the first and second sections 115, 120 is governed by the mechanicallinkage 515 consisting of hinged struts of lengths carefully chosen toallow section 505 to remain stationary while sections 115,120reciprocate. In particular, the axes of rotational motion of the hinges550, 552, 554 must be coplanar and must lie in a plane parallel to thedirection of relative motion of the sections 115,120 and osculating thecylindrical surface of the stationary section 505. Note that themechanical linkage 515 illustrated is but one means by which thestationary section 505 may be functionally tied to the first and secondsections 115, 120 and other means may be used in alternativeembodiments.

In one embodiment shown in FIG. 5C, the source 500 includes an umbilical520 that attaches to the stationary section 505 through a junction box525. The umbilical 520 runs from the surface, typically a survey vesselsuch as the vessel 210 in FIG. 2, and includes leads for the compressedgas, control, and power as described above. These are continued from thejunction box 525 to a penetration 540 mounted on one of the movingsections 115,120 via highly flexible leads 531-533. These leads 531-533should not impede the reciprocating motion of the two sections 115, 120and should be resistant to fatigue caused by the relative motion of thesections 115, 120, 505. They may for example be coiled. They enter thesection 115 or 120 via the penetration 540 and connect to equipmenttherein. Other considerations, such as water tightness and weightdistribution, applicable to embodiments described above, also apply.Note that the umbilical 520 permits the removal of some components foundin some embodiments from the depicted source 500 to, for example, thesurvey vessel.

Returning to FIG. 5A-FIG. 5C, not shown therein is ancillary equipmentsuch as hydraulic power supplies and accumulators, electrictransformers, etc. This ancillary equipment may conveniently be mountedon a skid or other mounting means attached to the central section andsituated underneath it. The device would rest on this when on deck or onland.

Some embodiments, such as the seismic source 700 in FIG. 7, may bedesigned to have more than one degree of freedom of vibration within thefrequency range. One may, for example, attach masses 705 (only oneindicated) on springs 710 (only one indicated) to one or both sections115, 120 of the casing 105. The masses could be positioned in annulithat slide along the push-pull rod 160 on linear bearings 715 (only oneindicated). Each mass/spring combination will use its own excitationactuator (not shown). Note that these components should be disposed inthe chamber 145 evenly enough to maintain the roughly equal masses ofthe first and second sections 115, 120.

The masses 705 should be near the center of the device 700 to avoidchanging the trim of the device 700. The masses 705 will affect thedynamics of the fundamental resonance, for which other aspects of thedesign as discussed above should compensate. The masses 705 may alsoincrease negative buoyancy, and so their size should be minimized. Ifthe suspension (i.e., spring 710 plus bearing 715) is sufficientlylow-loss, the masses 705 can be smaller with an increased travel to getthe same forces. For example, we could use a mass 705 with a fifth themass of the casing 105, travelling five times as far, to get the sameforce on the casing 105. Steel springs are low-loss and linear, and,hence, are well suited.

This mass/spring mechanism cannot be adjusted once the seismic source700 is deployed. Thus, if the frequency changes (e.g., if the depth orthe mass is changed), they will not track the change and modify theiroperation accordingly. This could be addressed by using gas springs (notshown), with their equilibrium pressure maintained equal to the pressurein the main gas space so that they do track. However, they will havehigher losses than steel springs (seal friction), and they will not belinear. This may make it harder to reduce the oscillating mass by usinglarge travels. It will increase the power of the extra actuators neededto drive the masses. Their frequency may drift as friction heats up thegas in the springs unless the pressure control is very good. It willalso mean that to some extent, unwanted higher harmonics will begenerated.

The velocities of the linear bearings 715 will be high. A brass plainbearing may manage a velocity of 6 m/s. For higher speeds, magnetic orhydrodynamic bearings might be needed.

The “transfer impedance” between the two ends of the seismic source 700(if one end creates a pressure in the water, it acts on the other) maymodify the output of the harmonics. It is anticipated that this effectwill not be significant.

The following patent applications and patents are hereby incorporated byreference for those portions that are listed and for the purposes setforth as if set forth verbatim herein.

U.S. application Ser. No. 13/327,524, entitled, “Seismic AcquisitionUsing Narrowband Seismic Sources”, filed Dec. 15, 2011, in the name ofthe inventors Joseph A. Dellinger et al., published Jun. 21, 2012, asU.S. Patent Publication 2012/0155217, and commonly assigned herewith forits teachings regarding data acquisition located at ¶¶[0024]-[0040],[0054]-[0059], [0065]-[0088].

U.S. Pat. No. 8,387,744, entitled, “Marine Seismic Source”, and issuedMar. 5, 2013, to BP Corporation of North America as assigned of theinventors Mark Harper et al. and commonly assigned herewith, for itsteachings regarding the design of the domed ends of the source disclosedtherein found in column 6, line 64 to column 8, line 11.

To the extent that any patent, patent application or paper incorporatedby reference herein conflicts with the present disclosure, the presentdisclosure controls.

Other embodiments of the invention will be apparent to those skilled inthe art from consideration of the specification and practice of theinvention disclosed herein. It is intended that the specification andexamples be considered as exemplary only, with a true scope and spiritof the invention being indicated by the following claims.

1. A compact marine seismic source for seismic acquisition generating ahumming signal, the source comprising: a casing defining a gas filledfluid tight chamber and comprised of a first casing section and a secondcasing section of roughly equal mass; a controller; a low-frequencyreciprocating drive disposed within the fluid tight chamber that, inoperation, reinforces the natural reciprocating oscillation of the firstand second casing sections relative to one another at a low frequency toomni-directionally radiate a low frequency, humming seismic signal; andwherein a frequency of the source is controlled by adjusting a tow depthof the source using the controller.
 2. The compact seismic source ofclaim 1, wherein the first and second sections are joined by a slidingfluid tight seal allowing relative motion.
 3. The compact seismic sourceof claim 1, wherein the first and second casing sections each include ahemispherically-domed end.
 4. The compact seismic source of claim 1,wherein the reciprocating drive comprises: an excitation actuatordisposed in the first casing section; and a push-pull rod mechanicallylinked to the excitation actuator at one end thereof and affixed to thesecond casing section at a second end thereof
 5. The compact seismicsource of claim 4, further comprising: at least one bearing for thepush-pull rod disposed in the first casing section; and a guide for thepush-pull rod disposed in the second casing section.
 6. The compactseismic source of claim 1, further comprising: a gas reservoiroperationally coupled to the chamber; and an excitation actuator;wherein the controller is electrically connected to the gas reservoirand the excitation actuator to control their operation includingcontrolling a resonating frequency for the compact seismic source. 7.The compact seismic source of claim 1, further comprising a plurality offluid tight chambers within at least one of the first casing section orsecond casing section, the plurality of fluid-tight chambers in fluidcommunication with each other via a controllable valve.
 8. The compactseismic source of claim 7, wherein volumes of the fluid-tight chambersare arranged in a powers-of-two distribution.
 9. The compact seismicsource of claim 1, further comprising masses free to vibratelongitudinally on springs. 10-21. (canceled)
 22. The compact seismicsource of claim 1, wherein the controller is electrically connected tothe compact seismic source via an umbilical.
 23. The compact seismicsource of claim 1, wherein the controller is housed within the casing.24. The method of claim 1, wherein omni-directionally radiating the lowfrequency seismic signal includes omni-directionally radiating alow-frequency seismic signal in the range of 0.5-2 Hz.